US10215271B2 - Planetary gear - Google Patents

Planetary gear Download PDF

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Publication number
US10215271B2
US10215271B2 US13/139,958 US200913139958A US10215271B2 US 10215271 B2 US10215271 B2 US 10215271B2 US 200913139958 A US200913139958 A US 200913139958A US 10215271 B2 US10215271 B2 US 10215271B2
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Prior art keywords
planetary gear
stage
input
gear according
sun wheel
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US13/139,958
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US20110251010A1 (en
Inventor
Andreas Grimm
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SEW Eurodrive GmbH and Co KG
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SEW Eurodrive GmbH and Co KG
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Assigned to SEW-EURODRIVE GMBH & CO. KG reassignment SEW-EURODRIVE GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GRIMM, ANDREAS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/047—Sliding-contact bearings for exclusively rotary movement for axial load only with fixed wedges to generate hydrodynamic pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears

Definitions

  • the present invention relates to a planetary gear.
  • DE 23 05 780 describes a multi-stage planetary gear, in which the planet wheels are held on the pins of the planet carriers and the individual stages are held against one another by a slide ring system.
  • DE 33 30 337 describes a power turning device, which has a housing part, in which a single-stage or multi-stage main gear is located. At the input side of the housing part, a housing part is fastened in a detachable manner, which contains an additional gear stage.
  • U.S. Pat. No. 4,437,530 describes an axle drive device for driving vehicle wheel devices, which includes a differential mechanism for driving axle shafts.
  • the planetary gear includes at least two sun wheels, which are disposed coaxially one behind the other, a hydrodynamic axial bearing being arranged between the sun wheels.
  • the hydrodynamic axial bearing is arranged between two mutually facing end faces of the sun wheels. It is advantageous in this regard that no additional components are required.
  • a first of the sun wheels has a first recess in its end face, which in the circumferential direction partially extends further radially than the end face of a second of the sun wheels. It is advantageous in this regard that the sections of the end faces, which form the hydrodynamic axial bearing, are well supplied with lubricant.
  • the first recess is situated concentrically to the axle of the first sun wheel and is preferably arranged to have an oval shape. It is advantageous in this regard that the first recess is simple to produce and the hydrodynamic axial bearing is supplied with lubricant or is arranged in a uniformly symmetrical manner.
  • a centrally disposed pin projects beyond the end face of the second sun wheel, which is situated at least partially in another recess of the end face of the first sun wheel. It is advantageous in this regard that the production of the second sun wheel is simplified since the pin is also usable as a holding device for a tool in the manufacture.
  • bank-up steps are formed for the hydrodynamic axial bearing, which ensure a good lubricant supply and ensure that the lubricant remains between the regions of the end faces that form the hydrodynamic axial bearing.
  • the additional recess is arranged concentrically to the axis of the first sun wheel and in a circular manner, the additional recess extending axially deeper into the first sun wheel than the first recess. It is advantageous in this regard that the additional recess is suitable for receiving the pin. At the same time, the additional recess is suitable as a lubricant reservoir for the hydrodynamic axial bearing.
  • a level of an oil, with which the planetary gear is at least partially filled touches at least the first recess or the first recess is at least immersed in the lubricant, in particular oil. It is advantageous in this regard that the hydrodynamic axial bearing is provided reliably out of a position of rest of the planetary gear.
  • centering bores and/or tool receptacles are produced in the end faces of the sun wheels. It is advantageous in this regard that the sun wheels are readily handled in the manufacture. Furthermore, the centering bores act as a lubricant reservoir for the hydrodynamic axial bearing.
  • a distance between a front surface of the pin and a bottom surface of the additional recess is greater than the distance between the mutually facing end faces. It is advantageous in this regard that the hydrodynamic axial bearing is well-defined, i.e. is not overdetermined in its position, and that a lubricant reservoir, in particular an oil reservoir, is formed for the hydrodynamic axial bearing.
  • the sun wheels are supported in an axially floating manner. It is advantageous in this regard that the sun wheels are simple to mount and that the hydrodynamic axial bearing is arranged differently depending on a rotational speed difference of the sun wheels.
  • an input-side end region of one of the sun wheels, in particular the second sun wheel is connected with a corresponding end region of an input shaft or of a planet carrier of a preceding planetary stage in a rotationally fixed, preferably form-locking manner. It is advantageous in this regard that a torque is securely transmittable and that axial forces on the input shaft or the planet carrier of a preceding planetary stage are absorbed by the hydrodynamic axial bearing.
  • the planetary gear has a first and a second stage, a first sun wheel engaging with an end region as an engaging piece into a planet carrier of the first stage, the first sun wheel having a continuous toothing in the axial direction. It is advantageous in this regard that the planetary gear is simple to manufacture.
  • the first sun wheel has a central region, where the continuously manufactured toothing is interrupted. It is advantageous in this regard that a two-cheeked planet carrier is producible with greater strength.
  • the end region has in a subregion a shortened crown circle, which produces an axial stop. It is advantageous in this regard that the first sun wheel is disposed in a well-defined manner with respect to the planet carrier of the first stage. Axial forces are transmittable onto the first sun wheel at least in one direction.
  • the second stage is arranged as an output stage, a two-cheeked planet carrier of the output stage being provided on the output side as a hollow shaft, which preferably encloses a shrink disk, or as a solid shaft, particularly as a solid square shaft. It is advantageous in this regard that a torque is securely transmittable.
  • an intermediate flange is arranged as a cast part, on which a first internal gear for the first stage and a second internal gear for the second stage are flange-mounted. It is advantageous in this regard that the intermediate flange is producible in a stable and cost-effective manner.
  • an input stage is disposed in front of the first stage when viewed from the input side. It is advantageous in this regard that a greater transmission ratio range is realizable in a variable manner using the input stage as the zeroth stage of the planetary gear.
  • the second sun wheel engages as a sun wheel of the first stage in an input-side end region with a multiple spline toothing into a planet carrier of the input stage. It is advantageous in this regard that the torque is securely transmittable from the input stage into the first stage.
  • the input stage and the first stage each have three planet wheels. It is advantageous in this regard that a torque is securely transmittable.
  • the second stage has four planet wheels. It is advantageous in this regard that a greater torque is transmittable or that the wear is reduced.
  • an input cover has a central cylinder jacket-shaped bearing carrier and a circular shield part enclosing the bearing carrier, the shield part being reinforced by triangular parts projecting radially from the bearing carrier, and the triangular parts being supported on the bearing carrier. It is advantageous in this regard that radial forces may be safely dissipated.
  • an equal-sided triangular input planet carrier is produced as a cast part together with planet bolts for bearing the input planet wheels of the input stage, the planet bolts being manufacturable from the cast part in varying radial distances to a central a axis of the planetary gear. It is advantageous in this regard that varying transmission ratios are implementable in a simple manner.
  • the planet carriers of the first and second stage are cast as one piece, receiving holes for the bolts or additional bolts for the planet wheels being producible at different radial distances to a central axis of the planetary gear. It is advantageous in this regard that varying transmission ratios are implementable in a simple manner.
  • a housing of the planetary gear includes an input-side cover, an input internal gear, an input flange, a first internal gear, an intermediate flange, a second internal gear and an output cover, the input flange, the intermediate flange and the output cover each being produced from one cast part or forged part. It is advantageous in this regard that the housing of the planetary gear may be manufactured in a simple and cost-effective manner.
  • FIG. 1 is an exploded view of a planetary gear according to an example embodiment of the present invention.
  • FIG. 2 is a front view and a side view of the example embodiment shown in FIG. 1 .
  • FIG. 3 is a front view and a side view of another example embodiment.
  • FIG. 4 is an exploded view of another example embodiment.
  • FIG. 5 is a front view and a side view of the example embodiment shown in FIG. 4 .
  • FIG. 6 is a front view and a side view of a modified example embodiment.
  • FIG. 7 illustrates two sun wheels of the planetary gear according to an example embodiment of the present invention in an exploded view.
  • FIG. 8 is a sectional view of the sun wheels shown in FIG. 7 .
  • FIG. 1 shows a planetary gear 10 according to an example embodiment of the present invention in an exploded view.
  • Planetary gear 10 comprises three stages: a zeroth stage as input stage 80 , a first stage 20 , which functions as an alternative input stage if the zeroth stage is not present, and a second stage 30 as output stage.
  • a housing of planetary gear 10 includes an input-side cover 17 , on which an input internal gear 16 is fastened. On its output side, an input flange 81 is screwed on input internal gear 16 . On its output side, the input flange is followed by a first internal gear 11 , which is fastened by a screw 15 on an intermediate flange 13 . Intermediate flange 13 forms the connection from a second internal gear 12 to first internal gear 11 .
  • Second internal gear 12 is screwed to intermediate flange 13 by another screw 19 .
  • second internal gear 12 is followed by an output cover 18 , which closes off the housing of planetary gear 10 on the output side.
  • An air vent 72 and a screw plug 74 are situated on the housing. The air vent is used for pressure equalization when an interior of planetary gear 10 heats up.
  • the opening in the housing of planetary gear 10 which is closed by screw plug 74 , is used for pouring in or exchanging a lubricant, preferably oil, of planetary gear 10 .
  • the input flange 81 , the intermediate flange 13 and the output cover 18 are preferably made from cast parts.
  • the input flange 81 , the intermediate flange 13 and the output cover 18 are preferably arranged as forged parts.
  • An input shaft 82 projects through input cover 17 .
  • An end region on the output side is developed to be hollow.
  • the input cover 17 has a central cylinder jacket-shaped bearing carrier and a circular shield part enclosing the bearing carrier.
  • the shield part is reinforced by triangular parts projecting radially from the bearing carrier. The triangular parts are supported on the bearing carrier.
  • Input shaft 82 is supported by an input shaft bearing 84 in the bearing carrier of input cover 17 .
  • input shaft bearing is covered by a cap 86 .
  • Cap 86 has a seal toward input shaft 82 .
  • Input stage 80 of planetary gear 10 is situated in input internal gear 17 .
  • An input sun wheel 91 engages with an input-side subregion, which has a multiple spline toothing, into a corresponding opening in input shaft 82 .
  • Input sun wheel 91 mates by a toothed region with three input planet wheels 92 .
  • Input planet wheels 92 are supported by a planet bearing 94 on planet bolts 96 of an input planet carrier 90 and are engaged with a toothing of input internal gear 16 .
  • Input planet carrier 90 is arranged as an approximately equal-sided triangle having a central circular opening.
  • Planet bolt 96 is formed directly from the cast part.
  • a raw cast part for manufacturing input planet carrier 90 has raw bolts projecting axially, which reveal a base area elongated in an oval shape in the radial direction when viewed from the axial perspective.
  • planet bolts 96 from the raw bolts at varying radial distances to a central axis of planetary gear 10 .
  • Input stage 80 is followed by first stage 20 of planetary gear 10 .
  • a second sun wheel 22 of the first stage projects with an end region is arranged as multiple spline toothing into the circular opening of input planet carrier 90 .
  • the circular opening has a corresponding multiple spline toothing.
  • a toothed region of second sun wheel 22 mates with a planet wheel 27 .
  • Planet wheel 27 is supported on bolt 24 of a planet carrier 26 of first stage 20 via a planet wheel bearing 28 and is engaged with a toothing of first internal gear 11 .
  • Planet wheel bearing 28 is axially fixed by respective retaining rings.
  • Bolts 24 are situated in corresponding openings in cheeks of planet carrier 26 , which is preferably arranged to have two cheeks.
  • First stage 20 preferably has three planet wheels 27 .
  • a second stage 30 is situated on the output side in the central cylinder jacket-shaped housing part 12 .
  • a first sun wheel 32 in principle has a continuously manufactured toothing.
  • the continuously manufactured toothing of first sun wheel 32 is interrupted by a recess in a central region 36 of first sun wheel 32 .
  • interrupted means that no toothing is present at all, that is, that first sun wheel 32 has a—within the limits of manufacturing precision—smooth surface in this central region 36 , a diameter of first sun wheel 32 in this central region 36 corresponding at most to the root-circle diameter of the adjacent toothing.
  • first sun wheel 32 is clamped and the toothing machine guides the cutting tool with an uninterrupted lifting motion over the entire axial length of first sun wheel 32 . Because of the recess, less material has to be removed.
  • An input-side end region 34 of first sun wheel 32 has shortened teeth in a subregion 35 , which thus form a reduced crown-circle diameter.
  • first sun wheel 32 engages into planet carrier 26 of the first stage.
  • planet carrier 26 of the first stage 20 has a corresponding toothing in a circular opening in the output-side cheek. Centering occurs via the tooth faces.
  • the possible fits are a clearance fit, a transitional fit or a press fit. For example embodiments having a particular low backlash, a cutting fit is possible as well.
  • the shortened crown circle in subregion 35 produces an axial stop 38 , on which planet carrier 26 abuts with an output-side end face.
  • First sun wheel 32 is supported in a two-cheeked planet carrier 40 of the second stage 30 with an output-side end section by a sun wheel bearing 33 , which is preferably arranged as a grooved ball bearing.
  • a sun wheel bearing 33 which is preferably arranged as a grooved ball bearing.
  • another planet wheel 41 is supported on another bolt 49 via a bolt bearing 47 .
  • the additional bolt 49 is held in openings in the cheeks of two-cheeked planet carrier 40 .
  • Preferably two double-cylinder roller bearings are provided as bolt bearing 47 between the additional bolt 49 and additional planet wheel 41 .
  • Additional planet wheel 41 mates with first sun wheel 32 .
  • the toothing of sun wheel 32 is ground only in the region, where first sun wheel 32 mates with additional planet wheel 41 .
  • the recess between the non-ground input-side region 34 and the ground region allows for the grinding tool to be more readily guided away from and guided toward first sun wheel 32 in the manufacture.
  • FIGS. 7 and 8 show details of first sun wheel 32 and second sun wheel 22 .
  • First sun wheel 32 and second sun wheel 22 are situated coaxially one behind the other.
  • a hydrodynamic axial bearing is arranged between the mutually facing end faces on account of the different rotational speeds during the operation of the planetary gear.
  • a first recess 37 is formed, in particular milled, in the end face of first sun wheel 32 . As may be seen from FIG. 8 , first recess 37 extends beyond the end face of second sun wheel 22 . That is to say, the radial outer regions of first recess 37 may be seen when looking from the axial direction from second sun wheel 22 . This makes it possible for a lubricant, preferably a lubricating oil or oil, with which planetary gear 10 is at least partly filled, to penetrate first recess 37 .
  • first sun wheel 32 and second sun wheel 22 of planetary gear 10 Due to the different rotational speeds of first sun wheel 32 and second sun wheel 22 of planetary gear 10 during the operation of planetary gear 10 , the penetrating lubricant is drawn between the mutually facing end faces of first sun wheel 32 and second sun wheel 22 and there forms a lubricating film. This produces a pressure in the axial direction, which forms the hydrodynamic axial bearing.
  • a lubricant level is at least at the level of the radial extension of first recess 37 . This ensures that when planetary gear 10 starts up the lubricant is conveyed between the end faces on account of the different rotational speed of the first and the second sun wheel 32 , 22 .
  • First recess 37 is preferably situated concentrically to the axis of first sun wheel 32 and arranged in an oval shape. This produces a symmetrical lubricating film, and the hydrodynamic axial bearing is provided more advantageously.
  • first sun wheel 32 has another recess 39 , which is arranged concentrically to the axis of first sun wheel 32 and in a circular manner.
  • the additional recess 39 extends further into first sun wheel 32 than first recess 37 .
  • additional recess 39 extends symmetrically beyond first recess 37 .
  • a blind-end bore is produced in a bottom of additional recess 39 , which is used to fasten and/or center first sun wheel 32 in a tool.
  • a pin 23 of the end face of second sun wheel 22 extends at least partly into additional recess 39 .
  • Pin 23 protrudes concentrically, centrally from the end face of second sun wheel 22 .
  • Pin 23 is used to fasten second sun wheel 22 in a tool. Cutting this pin 23 off is more involved that machining the end face of first sun wheel 32 with another recess 39 .
  • Pin 23 additionally supports the arrangement of the hydrodynamic axial bearing as a bank-up step for the lubricant.
  • Respectively one centering bore is produced in the mutually facing end faces. This is used for centering and/or as an attachment aide for a tool in the manufacture of sun wheels 22 , 32 . At the same time, these centering bores extend a lubricant reservoir for the hydrodynamic axial bearing.
  • two-cheeked planet carrier 40 is supported by a planet carrier bearing 43 in intermediate flange 13 .
  • planet carrier 43 is arranged either as a hollow shaft 42 or a solid shaft 46 .
  • Solid shaft 46 or hollow shaft 42 protrudes with another end section from output cover 18 and is supported in output cover 18 via an output bearing 45 .
  • a shaft sealing ring 70 preferably a double shaft sealing ring, is situated between solid shaft 46 or hollow shaft 42 and output cover 18 for the purpose of sealing.
  • Shaft sealing ring 70 is provided on a race 71 situated on hollow shaft 42 .
  • shaft sealing ring 70 is covered or protected by a sheet metal part 73 .
  • a shrink disk 44 surrounds the further end section of hollow shaft 42 at least partly for the purpose of fastening a device that is to be driven.
  • a cylinder jacket-shaped cover is attachable to output cover 18 in order to prevent injury.
  • the cylinder jacket-shaped cover is preferably, in particular exclusively, manufactured from bent parts that are screwed together.
  • An L-shaped foot may be screwed onto output cover 18 .
  • the L-shaped foot has an approximately annular subsection and a rectangular frame as a base or fastening surface.
  • the annular subsection includes protuberances, on which the rectangular frame is fastened. Additionally, the approximately annular subsection and the rectangular frame are connected to each other via an angular bracket. An end region of the angular bracket projects through a rectangular slot of a protuberance on the approximately annular subsection. Both parts are preferably welded to each other. This facilitates mounting the L-shaped foot.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)
US13/139,958 2008-12-15 2009-12-09 Planetary gear Active 2033-03-07 US10215271B2 (en)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE102008061903 2008-12-15
DE102008061903. 2008-12-15
DE122009042591.8 2009-09-24
DE102009042591 2009-09-24
DE102009042591A DE102009042591B4 (de) 2008-12-15 2009-09-24 Planetengetriebe
PCT/EP2009/008783 WO2010072331A1 (de) 2008-12-15 2009-12-09 Planetengetriebe
DE102008061903 2018-12-15

Publications (2)

Publication Number Publication Date
US20110251010A1 US20110251010A1 (en) 2011-10-13
US10215271B2 true US10215271B2 (en) 2019-02-26

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Application Number Title Priority Date Filing Date
US13/139,958 Active 2033-03-07 US10215271B2 (en) 2008-12-15 2009-12-09 Planetary gear

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US (1) US10215271B2 (pt)
EP (1) EP2376806B1 (pt)
CN (1) CN102245930B (pt)
AU (1) AU2009331938B2 (pt)
BR (1) BRPI0922603B1 (pt)
DE (1) DE102009042591B4 (pt)
WO (1) WO2010072331A1 (pt)
ZA (1) ZA201103788B (pt)

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US20220316575A1 (en) * 2021-03-30 2022-10-06 Dana Belgium N.V. Sun gear for use in a planetary gear system, counter bearing part, bearing arrangement and planetary gear system

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DE102016220952A1 (de) * 2016-10-25 2018-04-26 Volkswagen Aktiengesellschaft Antriebsstrang, insbesondere Hybridantriebsstrang für ein Kraftfahrzeug
CN108547917A (zh) * 2018-07-14 2018-09-18 广西宏太智能机器人制造有限公司 一种可无限叠加的行星减速器
EP3830451B1 (de) * 2018-07-31 2022-09-07 Sew-Eurodrive GmbH & Co. KG Getriebe mit zumindest einer planetengetriebestufe
CN108953507B (zh) * 2018-09-18 2020-05-19 浙江东方机电有限公司 一种减速比可调的齿轮减速器
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DE102020203347B3 (de) * 2020-03-16 2021-07-08 Zf Friedrichshafen Ag Axiallager zwischen zwei Sonnenwellen
CN114623207B (zh) * 2022-03-02 2024-09-03 南京高精齿轮集团有限公司 一种齿轮箱结构
CN115163809B (zh) * 2022-09-08 2022-11-25 常州市曼多林精密机械科技有限公司 一种高精密微米行星减速机

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US20220316575A1 (en) * 2021-03-30 2022-10-06 Dana Belgium N.V. Sun gear for use in a planetary gear system, counter bearing part, bearing arrangement and planetary gear system
US11821505B2 (en) * 2021-03-30 2023-11-21 Dana Belgium N.V. Sun gear for use in a planetary gear system, counter bearing part, bearing arrangement and planetary gear system

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BRPI0922603A2 (pt) 2015-12-22
DE102009042591A1 (de) 2010-06-17
DE102009042591B4 (de) 2012-12-06
AU2009331938A1 (en) 2010-07-01
BRPI0922603B1 (pt) 2019-04-16
AU2009331938B2 (en) 2015-01-15
EP2376806B1 (de) 2012-12-05
ZA201103788B (en) 2012-07-25
WO2010072331A1 (de) 2010-07-01
CN102245930B (zh) 2014-07-16
US20110251010A1 (en) 2011-10-13
CN102245930A (zh) 2011-11-16

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